EP2719916A1 - Ventilstruktur - Google Patents

Ventilstruktur Download PDF

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Publication number
EP2719916A1
EP2719916A1 EP12796069.8A EP12796069A EP2719916A1 EP 2719916 A1 EP2719916 A1 EP 2719916A1 EP 12796069 A EP12796069 A EP 12796069A EP 2719916 A1 EP2719916 A1 EP 2719916A1
Authority
EP
European Patent Office
Prior art keywords
valve
ports
piston
side chamber
pressure side
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP12796069.8A
Other languages
English (en)
French (fr)
Other versions
EP2719916A4 (de
Inventor
Yukimasa KOBAYASHI
Hideaki Takeuchi
Yoshihiro Shibata
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KYB Corp
Original Assignee
Kayaba Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kayaba Industry Co Ltd filed Critical Kayaba Industry Co Ltd
Publication of EP2719916A1 publication Critical patent/EP2719916A1/de
Publication of EP2719916A4 publication Critical patent/EP2719916A4/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/3405—Throttling passages in or on piston body, e.g. slots
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
    • F16F9/3481—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by shape or construction of throttling passages in piston

Definitions

  • the present invention relates to improvement of a valve structure.
  • a valve structure is applied, for example, to a piston portion of a damper for a vehicle, and the like.
  • JP2006-194335A discloses a valve structure including a piston P slidably inserted into a cylinder C of a damper and partitioning an interior of the cylinder C into an extension side chamber ER and a pressure side chamber CR, pluralities of extension side ports EP and pressure side ports CP provided in the piston P and communicating between the extension side chamber ER and the pressure side chamber CR, an annular extension side leaf valve EL laminated in a pressure side chamber end of the piston P and opening and closing only the extension side ports EP, and an annular pressure side leaf valve CL laminated in an extension side chamber end of the piston P and opening and closing only the pressure side ports CP, wherein the extension side ports EP and the pressure side ports CP are alternately arranged along the circumferential direction of the piston P.
  • Some members forming the damper require cutting processing, and iron powder generated at the time of the cutting processing may sometimes remain attached to such members. Dust may sometimes remain attached to parts. Therefore, mixture of the contaminants Co is not easily completely prevented.
  • JP2005-76856A discloses that a bag shape or pocket shape foreign substance reservoir for collecting the contaminants Co is provided in a piston or a valve case installed in an end of a cylinder. However, since the working oil cannot flow into this foreign substance reservoir, the contaminants Co are not easily collected.
  • An object of the present invention is to provide a valve structure capable of preventing generation of a noise.
  • a valve structure comprises a valve disc partitioning an interior of a damper into a one-side chamber and an other-side chamber; a plurality of one-side ports provided in the valve disc and communicating between the one-side chamber and the other-side chamber; a plurality of other-side ports provided in the valve disc and communicating between the one-side chamber and the other-side chamber; an annular one-side leaf valve laminated in an other-side chamber end of the valve disc and opening and closing only the one-side ports; and an annular other-side leaf valve laminated in a one-side chamber end of the valve disc and opening and closing only the other-side ports, wherein the one-side ports and the other-side ports are alternately arranged in the valve disc along the circumferential direction, and a plurality of through holes formed in the valve disk is opened from the inner circumferential side of openings of all the other-side ports in the one-side chamber end of the valve disc and communicates with the one-side ports.
  • the valve structure in the present embodiment is applied to a piston portion of the damper.
  • the valve structure includes a piston 1 (valve disc) partitioning an interior of the damper into an extension side chamber R1 (one-side chamber) and a pressure side chamber R2 (other-side chamber), a plurality of extension side ports 2 (one-side ports) provided in the piston 1 and communicating between the extension side chamber R1 and the pressure side chamber R2, a plurality of pressure side ports 3 (other-side ports) provided in the piston 1 and communicating between the extension side chamber R1 and the pressure side chamber R2, an annular extension side leaf valve 4 (one-side leaf valve) laminated in a pressure side chamber end b (other-side chamber end) of the piston 1 and opening and closing only the extension side ports 2, and an annular pressure side leaf valve 5 (other-side leaf valve) laminated in an extension side chamber end a (one-side chamber end) of the piston 1 and opening and closing only the pressure side ports 3, and a plurality of through holes 6 opened
  • extension side chamber R1 is a chamber to be compressed at the time of an extension operation of the damper
  • pressure side chamber R2 is a chamber to be compressed at the time of a contraction operation of the damper.
  • a sectional view of the piston 1 of Fig. 1 is a sectional view by arrow A-A of the piston 1 shown in Fig. 2 .
  • the damper includes, for example, a cylinder 40, a head member (not shown) sealing an upper end of the cylinder 40, a piston rod 10 slidably passing through the head member, the above piston 1 provided in an end of the piston rod 10, the extension side chamber R1 and the pressure side chamber R2 serving as two pressure chambers formed by partitioning an interior of the cylinder 40 by the piston 1, a sealing member (not shown) sealing a lower end of the cylinder 40, and a reservoir or an air chamber (not shown) compensating a volume change in the cylinder corresponding to a volume of the piston rod 10 projecting and retracting from the cylinder 40.
  • a fluid, specifically working oil is charged into the cylinder 40.
  • the damper may be not a single rod type but a double rod type.
  • the piston 1 is formed in an annular shape and assembled to the piston rod 10 by inserting a small diameter portion 10a formed in a leading end of the piston rod 10 into the inner side of the piston 1.
  • An outer circumference of the piston 1 is in sliding contact with an inner circumference of the cylinder 40. Thereby, the piston 1 partitions the interior of the cylinder 40 into the extension side chamber R1 and the pressure side chamber R2.
  • the piston 1 is formed in a bottomed tubular shape, and an insertion hole 1e into which the piston rod 10 is inserted, the four extension side ports 2, and the four pressure side ports 3 are provided in a bottom portion 1a.
  • the extension side ports 2 and the pressure side ports 3 respectively pass through the bottom portion 1a in the piston 1 in the up and down direction as the axial direction, so as to communicate between the extension side chamber R1 and the pressure side chamber R2.
  • the extension side ports 2 are arranged at equal intervals along the circumferential direction in the bottom portion 1a of the piston 1, and the pressure side ports 3 are also arranged at equal intervals along the circumferential direction in the bottom portion 1a of the piston 1. That is, the extension side ports 2 and the pressure side ports 3 are alternately arranged along the circumferential direction of the piston 1.
  • a valve seat 8 surrounding the four pressure side ports 3 respectively independently from each other is provided in the extension side chamber end a of the bottom portion 1a of the piston 1, a valve seat 8 surrounding the four pressure side ports 3 respectively independently from each other is provided.
  • the valve seat 8 protrudes from the bottom portion 1a toward the side of the extension side chamber, and includes an annular portion 8a surrounding a periphery of the insertion hole 1e, and four seat portions 8b provided continuously to the annular portion 8a and formed in a fan shape when seen in a plan view.
  • Parts of the bottom portion 1a where no valve seat 8 is provided, that is, parts between the seat portion 8b and the seat portion 8b along the circumferential direction are recessed toward the side of the pressure side chamber, and the extension side ports 2 are opened in the parts.
  • projections 1f are respectively provided between the seat portion 8b and the seat portion 8b along the circumferential direction.
  • Independent windows 3a are respectively provided in extension side chamber ends of the pressure side ports 3, and the seat portions 8b of the valve seat 8 surround four sides of these independent windows 3a.
  • the extension side ports 2 are arranged on the inner circumferential side of a ring shape zone Z (part shown by diagonal lines in the figure) where the pressure side ports 3 are provided.
  • annular window 7 communicating with all pressure side chamber ends of the four extension side ports 2 is provided in the pressure side chamber end b of the bottom portion 1a of the piston 1. That is, the annular window 7 is formed in an annular recessed shape.
  • An annular valve seat 9 is provided on the outer circumferential side of this annular window 7 and on the inner circumferential side of all the pressure side ports 3.
  • the extension side ports 2 are arranged on the inner circumferential side of the ring shape zone where the pressure side ports 3 are provided. Thereby, the annular window 7 provided continuously to outlets of the extension side ports 2 can be surrounded by the annular valve seat 9.
  • the pressure in the extension side chamber R1 can be uniformly applied over the entire circumference of the extension side leaf valve 4 to be described later.
  • the four through holes 6 opened from the inner circumferential side of the independent windows 3a as ends of the pressure side ports 3 and leading to the extension side ports 2 are provided.
  • the through holes 6 pass thorough the bottom portion 1a of the piston 1 along the up and down direction (in Fig. 1 ) as the axial direction, and pressure side chamber ends thereof lead to the annular window 7.
  • the annular window 7 leads to the extension side ports 2 as described above.
  • Extension side chamber ends of the through holes 6 lead to dents 13 provided in the bottom portion 1a of the piston 1 and formed in a substantially rectangular shape in a plan view ( Fig. 2 ).
  • the dents 13 are formed in such a manner that depth is gradually increased toward a center of the rectangle, and the extension side ports 2 are opened in the deepest parts.
  • the dents 13 are provided on the inner circumferential side of the independent windows 3a in the bottom portion 1a of the piston 1 so as to avoid contact with the independent windows 3a. Further, four sides of the dents 13 are surrounded by the seat portions 8b in the valve seat 8.
  • the installment number of the extension side ports 2 and the pressure side ports 3 is not limited to four described above.
  • the number can be set to the arbitrary number, and as many through holes 6 as the installment number of the pressure side ports 3 may be provided.
  • the through holes 6 may communicate with at least one of the plurality of extension side ports 2.
  • a plurality of annular grooves 1c is provided on an outer circumference of a tubular portion 1b of the piston 1.
  • a synthetic resin piston ring 11 is installed on the outer circumference of the tubular portion 1b.
  • the piston ring 11 is installed by heating and softening a disc shape synthetic resin base material while pressurizing and pushing into the outer circumference of the tubular portion 1b of the piston 1.
  • an annular recessed portion 1d may be provided in the tubular portion 1b, and an annular piston ring 12 having divisions in the annular recessed portion 1d may be installed.
  • Figs. 4 , 6 , 7, 8 show front views of the piston 1, a back view, a left side view, and a right side view are the same as the front view.
  • the piston 1 formed in such a way is assembled to the small diameter portion 10a of the piston rod 10.
  • the piston rod 10 is arranged in such a manner that the small diameter portion 10a in the leading end faces the lower side (in Fig. 1 ) of the piston 1, and a threaded portion 10b is provided in a further leading end of the small diameter portion 10a. Since a part on the upper side (in Fig. 1 ) of the small diameter portion 10a has a larger diameter than the small diameter portion 10a, a stepped portion 10c is formed on a border between this small diameter portion 10a and the part on the upper side of the small diameter portion 10a.
  • the extension side leaf valve 4 is formed by laminating a plurality of annular plates, and the inner circumferential side is fixed to the piston rod 10, so that warp of an outer circumference is allowed.
  • the uppermost annular plate (in Fig. 1 ) in the extension side leaf valve 4 in contact with the bottom portion 1a of the piston 1 is seated on the annular valve seat 9 so as to close the extension side ports 2.
  • an outer diameter of the extension side leaf valve 4 is set to such an extent that the pressure side ports 3 arranged on an outer circumference of the annular valve seat 9 are not closed.
  • the extension side leaf valve 4 is not in contact with pressure side chamber ends of the pressure side ports 3.
  • the pressure side leaf valve 5 is formed by laminating a plurality of annular plates, and the inner circumferential side is fixed to the piston rod 10, so that warp of an outer circumference is allowed.
  • the lowermost annular plate (in Fig. 1 ) in the pressure side leaf valve 5 in contact with the bottom portion 1a of the piston 1 is seated on the valve seat 8 so as to close the pressure side ports 3.
  • the parts of the valve seat 8 between the adjacent seat portions 8b are recessed toward the center direction of the piston 1 and the extension side ports 2 are opened in the parts.
  • the pressure side leaf valve 5 does not close the extension side ports 2 even when the pressure side leaf valve 5 close the pressure side ports 3.
  • the pressure side leaf valve 5 is pushed, warped, and separated from the seat portions 8b of the valve seat 8, so that the pressure side ports 3 are opened.
  • the parts in the bottom portion 1a of the piston 1 between the adjacent seat portions 8b of the valve seat 8 are recessed.
  • the pressure side leaf valve 5 receives the pressure of the extension side chamber R1
  • parts which are not supported by the seat portions 8b are warped in the direction in which the extension side ports 2 are closed.
  • the projections 1f protrude between the adjacent seat portions 8b and support the pressure leaf valve 5, a flow passage area of the extension side ports 2 is not limited.
  • extension side leaf valve 4 and the pressure side leaf valve 5 are formed by laminating the pluralities of annular plates, and warp rigidity can be adjusted by the number of lamination of the annular plates.
  • the number of lamination is arbitrarily set in accordance with a damping characteristic that the damper is required (characteristic of a damping force generated with respect to piston speed of the damper).
  • the inner circumferential side of the pressure side ports 3 leads to the extension side ports 2 via the through holes 6.
  • the pressure side chamber ends in the extension side ports 2 are closed by the extension side leaf valve 4 pushed to the piston 1 by the pressure of the pressure side chamber R2, and opposite extension side chamber ends always lead to the extension side chamber R1. Therefore, as shown by an arrow of Fig. 9 , a flow of the working oil passing from the pressure side ports 3 through to the through holes 6 and the extension side ports 2 and reaching to the extension side chamber R1 is generated.
  • the contaminants do not remain in a gap between the pressure side leaf valve 5 and the valve seat 8 provided in the piston 1 but are discharged to the through holes 6 by the above flow of the working oil.
  • the contaminants can be prevented from being nipped between the pressure side leaf valve 5 and the piston 1 and the pressure side leaf valve 5 can be prevented from being floated up from the piston 1.
  • generation of a large noise due to vibration of the outer circumference of the pressure leaf valve 5 can be prevented.
  • the pressure side leaf valve 5 can reliably close the pressure side ports 3. Thus, shortage of the damping force at the time of the extension operation of the damper can be prevented and the damping force can be stably obtained.
  • the dents 13 are respectively provided on the inner circumferential side of the openings of all the pressure side ports 3 and the through holes 6 are opened in the dents 13.
  • the annular window 7 leading to the openings of all the extension side ports 2 is provided in the pressure side chamber end b of the piston 1 and the through holes 6 are arranged so as to communicate with the extension side ports 2 via the annular window 7.
  • the through holes 6 can be formed along the axial direction with respect to the piston 1, drilling process for forming the through holes 6 becomes easier, and manufacturing cost of the piston to which the valve structure is applied can be reduced.
  • the through holes 6 are not limited to the above structure but may be provided obliquely to the axial direction of the piston 1 or bent in the middle as long as the through holes are opened from the inner circumferential side of the pressure side ports 3 and lead to the extension side ports 2.
  • the description is given with the one-side chamber serving as the extension side chamber R1, the other-side chamber serving as the pressure side chamber R2, the one-side ports serving as the extension side ports 2, the other-side ports serving as the pressure side ports 3, the one-side leaf valve serving as the extension side leaf valve 4, and the other-side leaf valve serving as the pressure side leaf valve 5.
  • the one-side chamber may be the pressure side chamber R2
  • the other-side chamber may be the extension side chamber R1
  • the one-side ports may be the pressure side ports 3
  • the other-side ports may be the extension side ports 2
  • the one-side leaf valve may be the pressure side leaf valve 5
  • the other-side leaf valve may be the extension side leaf valve 4.
  • a structure of the bottom portion 1a of the piston 1 becomes upside down in Fig. 1 .
  • a petal shape valve seat independently surrounding the pressure side ports 3 may be provided in the extension side chamber end a in the bottom portion 1a of the piston 1 and a petal shape valve seat independently surrounding the extension side ports 2 may be provided in the pressure side chamber end b in the bottom portion 1a of the piston 1.
  • a petal shape valve seat independently surrounding the extension side ports 2 may be provided in the pressure side chamber end b in the bottom portion 1a of the piston 1.
  • one of the one-side chamber and the other-side chamber can be a pressure side chamber of the damper
  • the other of the one-side chamber and the other-side chamber can be a reservoir for compensating volume of the damper
  • the valve disc can be a valve case of a base valve attached to an end of the cylinder of the damper and partitioning the pressure side chamber and the reservoir.
  • the dents 13 are respectively provided on the inner circumferential side of the openings of the pressure side ports 3 and the through holes 6 are opened in the dents 13.
  • the through holes 6 may be directly opened in the bottom portion 1a of the piston.
  • valve structure of the present invention can be utilized for a valve of a damper.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)
EP12796069.8A 2011-06-08 2012-05-22 Ventilstruktur Withdrawn EP2719916A4 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011127924A JP5695507B2 (ja) 2011-06-08 2011-06-08 バルブ構造
PCT/JP2012/063070 WO2012169343A1 (ja) 2011-06-08 2012-05-22 バルブ構造

Publications (2)

Publication Number Publication Date
EP2719916A1 true EP2719916A1 (de) 2014-04-16
EP2719916A4 EP2719916A4 (de) 2014-08-20

Family

ID=47295912

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12796069.8A Withdrawn EP2719916A4 (de) 2011-06-08 2012-05-22 Ventilstruktur

Country Status (6)

Country Link
US (1) US9033123B2 (de)
EP (1) EP2719916A4 (de)
JP (1) JP5695507B2 (de)
CN (1) CN103534507B (de)
TW (1) TWI553242B (de)
WO (1) WO2012169343A1 (de)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20130344A1 (it) * 2013-03-07 2014-09-08 Brera Cerniere Srl Ammortizzatore a fluido, particolarmente per sportelli di elettrodomestici come forni, lavastoviglie o simili o per componenti di arredamento come antine o cassetti, ad elevata semplicita' di realizzazione.
JP5603965B2 (ja) * 2013-03-25 2014-10-08 カヤバ工業株式会社 減衰バルブ
JP6754624B2 (ja) * 2016-06-15 2020-09-16 日立オートモティブシステムズ株式会社 緩衝器
US10239376B2 (en) 2016-09-22 2019-03-26 Beijingwest Industries Co., Ltd. Hydraulic damper with an x-flow piston assembly
US11035491B2 (en) 2017-07-03 2021-06-15 Continental Automotive Systems, Inc. Fuel pump solenoid having hydraulic damping
DE102017010876B4 (de) * 2017-11-24 2023-06-01 Günther Zimmer Zylinder-Kolben-Einheit mit lastabhängiger Drossel
JP6738368B2 (ja) * 2018-03-30 2020-08-12 Ｋｙｂ株式会社 バルブシート部材、バルブ、及び緩衝器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61164836U (de) * 1985-04-01 1986-10-13
JP2005076856A (ja) * 2003-09-03 2005-03-24 Honda Motor Co Ltd ダンパ装置
US20080314704A1 (en) * 2007-06-21 2008-12-25 Tenneco Automotive Operating Company, Inc. Junction bleed
US20100294604A1 (en) * 2009-05-20 2010-11-25 Kayaba Industry Co., Ltd. Damping mechanism

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4615420A (en) * 1984-01-23 1986-10-07 Ford Motor Company Piston assembly for shock absorber
GB2226620B (en) * 1988-10-25 1992-11-04 Tokico Ltd Hydraulic damper
JPH0292154U (de) 1989-01-10 1990-07-23
US5332069A (en) * 1989-08-31 1994-07-26 Kayaba Kogyo Kabushiki Kaisha Shock absorber
US5595269A (en) * 1993-05-10 1997-01-21 Fichtel & Sachs Ag Vibration damper for a motor vehicle
JP3471438B2 (ja) * 1993-12-06 2003-12-02 株式会社ショーワ 緩衝器のバルブ構造
JP3414090B2 (ja) * 1995-11-20 2003-06-09 トヨタ自動車株式会社 液圧緩衝器のバルブ構造
JP2006194335A (ja) 2005-01-13 2006-07-27 Kayaba Ind Co Ltd バルブ構造
US9022187B2 (en) * 2010-07-28 2015-05-05 Kayaba Industry Co., Ltd. Damping valve for shock absorber
TWM403579U (en) * 2010-12-14 2011-05-11 Yu Heng Engineering Co Ltd Energy dissipation device having throttle valve

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61164836U (de) * 1985-04-01 1986-10-13
JP2005076856A (ja) * 2003-09-03 2005-03-24 Honda Motor Co Ltd ダンパ装置
US20080314704A1 (en) * 2007-06-21 2008-12-25 Tenneco Automotive Operating Company, Inc. Junction bleed
US20100294604A1 (en) * 2009-05-20 2010-11-25 Kayaba Industry Co., Ltd. Damping mechanism

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2012169343A1 *

Also Published As

Publication number Publication date
CN103534507B (zh) 2015-04-01
JP5695507B2 (ja) 2015-04-08
US9033123B2 (en) 2015-05-19
TW201307700A (zh) 2013-02-16
CN103534507A (zh) 2014-01-22
US20140076677A1 (en) 2014-03-20
TWI553242B (zh) 2016-10-11
WO2012169343A1 (ja) 2012-12-13
EP2719916A4 (de) 2014-08-20
JP2012255467A (ja) 2012-12-27

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